WO2017199289A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2017199289A1 WO2017199289A1 PCT/JP2016/064488 JP2016064488W WO2017199289A1 WO 2017199289 A1 WO2017199289 A1 WO 2017199289A1 JP 2016064488 W JP2016064488 W JP 2016064488W WO 2017199289 A1 WO2017199289 A1 WO 2017199289A1
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- Prior art keywords
- refrigerant
- heat exchanger
- temperature
- indoor
- pressure
- Prior art date
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 44
- 239000003507 refrigerant Substances 0.000 claims abstract description 434
- 238000010438 heat treatment Methods 0.000 claims description 218
- 238000001816 cooling Methods 0.000 claims description 132
- 238000001514 detection method Methods 0.000 claims description 8
- 230000006837 decompression Effects 0.000 claims description 5
- 239000007788 liquid Substances 0.000 description 65
- 230000008859 change Effects 0.000 description 52
- 238000010257 thawing Methods 0.000 description 39
- 238000010586 diagram Methods 0.000 description 30
- 239000012071 phase Substances 0.000 description 25
- 230000002265 prevention Effects 0.000 description 25
- 239000002826 coolant Substances 0.000 description 22
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- 238000009833 condensation Methods 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 230000001771 impaired effect Effects 0.000 description 3
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- CDOOAUSHHFGWSA-OWOJBTEDSA-N (e)-1,3,3,3-tetrafluoroprop-1-ene Chemical compound F\C=C\C(F)(F)F CDOOAUSHHFGWSA-OWOJBTEDSA-N 0.000 description 2
- FXRLMCRCYDHQFW-UHFFFAOYSA-N 2,3,3,3-tetrafluoropropene Chemical compound FC(=C)C(F)(F)F FXRLMCRCYDHQFW-UHFFFAOYSA-N 0.000 description 2
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 2
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
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- 239000001282 iso-butane Substances 0.000 description 1
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- 229920006395 saturated elastomer Polymers 0.000 description 1
- 239000011555 saturated liquid Substances 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/10—Pressure
- F24F2140/12—Heat-exchange fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/20—Heat-exchange fluid temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/54—Heating and cooling, simultaneously or alternatively
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0251—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units being defrosted alternately
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
- F25B2313/02522—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses during defrosting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the present invention relates to an air conditioner that can simultaneously perform defrosting while continuing heating operation.
- heat pump type air conditioners that use air as a heat source have been introduced in place of boiler-type heaters that heat fossil fuels even in cold regions.
- the heat pump type air conditioner can efficiently perform heating as much as heat is supplied from the air in addition to the electric input to the compressor.
- frost forms on the outdoor heat exchanger serving as an evaporator. Therefore, it is necessary to perform defrost to melt the frost on the outdoor heat exchanger.
- the outdoor heat exchanger is configured by a plurality of parallel heat exchangers, and the other parallel heat exchanger is also in parallel while the other parallel heat exchanger is defrosted.
- a heat exchanger functions as an evaporator, heat is absorbed from air in the evaporator, and heating is performed (see, for example, Patent Document 1 and Patent Document 2).
- an outdoor heat exchanger is configured by a plurality of parallel heat exchangers in a cooling / heating switching type air conditioner that can perform either heating or cooling. Then, a part of the high-temperature refrigerant discharged from the compressor is alternately allowed to flow into each parallel heat exchanger, and each parallel heat exchanger is alternately defrosted, thereby continuously heating without reversing the refrigeration cycle. It is carried out.
- Patent Document 2 The technology described in Patent Document 2 is a simultaneous cooling and heating type air conditioner in which each indoor unit can perform heating or cooling.
- Patent Document 2 by configuring the outdoor heat exchanger with a plurality of parallel heat exchangers, heating is continuously performed without reversing the refrigeration cycle while defrosting some of the parallel heat exchangers. .
- a cooling / heating simultaneous operation (cooling / heating mixed operation) in which cooling and heating are performed simultaneously can be performed, and an operation according to an operation request in each room is possible.
- the pressure of the refrigerant that performs defrosting is either the same low pressure as the refrigerant that absorbs heat from the outside air or the same high pressure as the condenser, and cannot be adjusted to any other pressure. For this reason, when the saturation temperature of the refrigerant
- the flow rate of refrigerant flowing into the parallel heat exchanger to be defrosted must be increased. I must. When the flow rate of refrigerant flowing into the parallel heat exchanger to be defrosted is increased, the refrigerant flowing through the parallel heat exchanger on the heating side is insufficient, and the heating capacity is reduced. Moreover, when the pressure of the refrigerant
- the present invention has been made to solve the above-described problems, and can perform defrosting without stopping heating in simultaneous cooling and heating operations in which cooling and heating are performed simultaneously. It is an object to provide a cooling and heating simultaneous air conditioning apparatus capable of improving the comfort of the vehicle.
- a compressor, a plurality of indoor heat exchangers, a plurality of decompression devices, and an outdoor heat exchanger composed of a plurality of parallel heat exchangers are connected in order by piping.
- a first defrost pipe for supplying a main circuit and a part of the refrigerant discharged from the compressor to the parallel heat exchanger to be defrosted among the plurality of parallel heat exchangers;
- a first expansion device provided in the defrost pipe, a second defrost pipe for returning the refrigerant supplied to the parallel heat exchanger to be defrosted through the first defrost pipe to the main circuit, and a plurality of parallel heats
- the first flow path switching device for switching the connection on the compressor side in each of the exchangers to the first defrost pipe or the main circuit, and the connection on the opposite side of the compressor in each of the plurality of parallel heat exchangers, Switch to 2 defrost piping or main circuit
- the control device transfers a part of the refrigerant discharged from the compressor to the first defrost pipe and the second Pass through the defrost target parallel heat exchanger via the defrost pipe, and allow a plurality of parallel heat exchangers to function as an evaporator other than the defrost target parallel heat exchanger, and one of the plurality of indoor heat exchangers.
- the evaporator, the others First during operation to function as a condenser, in which the second throttle device and the third throttling device respectively individually controlled.
- defrosting can be performed without stopping heating in the simultaneous cooling and heating operation in which cooling and heating are performed simultaneously, and the second expansion device and the third expansion device are individually controlled.
- the comfort in both the cooling and heating rooms can be improved.
- FIG. 3 is a Ph diagram during a cooling operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. It is a figure which shows the flow of the refrigerant
- FIG. 3 is a Ph diagram during cooling-main operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- FIG. 2 is a Ph diagram during normal heating operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. It is a figure which shows the flow of the refrigerant
- FIG. 3 is a Ph diagram during heating-main normal operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- FIG. 5 is an explanatory diagram of the magnitude relationship between the pressure of a refrigerant that absorbs heat from outdoor air in the parallel heat exchanger 3-1.
- It is a refrigerant circuit diagram which shows the refrigerant circuit structure of the air conditioning apparatus 101 which concerns on Embodiment 2 of this invention.
- It is a refrigerant circuit diagram which shows the refrigerant circuit structure of the air conditioning apparatus 102 which concerns on Embodiment 3 of this invention.
- FIG. 1 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of an air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- the air conditioner 100 includes an outdoor unit (heat source unit, heat source side unit) A, a plurality of indoor units (load side units) B and C connected in parallel to each other, and a relay unit D.
- the outdoor unit A and the relay unit D are connected by a first extension pipe 31 that is a high-pressure pipe and a second extension pipe 32 that is a low-pressure pipe.
- the relay machine D and the indoor units B and C are connected by third extension pipes 33b and 33c and fourth extension pipes 34b and 34c.
- the air conditioner 100 is further provided with a control device 90.
- the control device 90 controls the cooling and heating switching of the indoor units B and C, the change of the set temperature, each switching device, a flow control device, a throttle device, and the like which will be described later.
- the control device 90 has a function of switching the operation mode by controlling each opening / closing device, flow rate control device, throttling device, and the like.
- the control device 90 can be configured by hardware such as a circuit device that realizes the function, or can be configured by an arithmetic device such as a microcomputer or a CPU and software executed thereon.
- the operation mode of the air conditioner 100 includes a cooling operation and a heating operation.
- the cooling operation includes a cooling only operation and a cooling main operation
- the heating operation includes a heating only operation and a heating main operation. Details of each of these operation modes will be described later.
- a chlorofluorocarbon refrigerant or an HFO refrigerant is used as the refrigerant.
- the chlorofluorocarbon refrigerant include R32 refrigerant, R125, and R134a, which are HFC refrigerants, and R410A, R407c, and R404A, which are mixed refrigerants thereof.
- the HFO refrigerant include HFO-1234yf, HFO-1234ze (E), and HFO-1234ze (Z).
- a vapor compression heat pump such as a CO 2 refrigerant, an HC refrigerant (for example, propane or isobutane refrigerant), an ammonia refrigerant, a mixed refrigerant of the above refrigerant such as a mixed refrigerant of R32 and HFO-1234yf, or the like.
- a vapor compression heat pump such as a CO 2 refrigerant, an HC refrigerant (for example, propane or isobutane refrigerant), an ammonia refrigerant, a mixed refrigerant of the above refrigerant such as a mixed refrigerant of R32 and HFO-1234yf, or the like.
- the refrigerant used in the above is used.
- Embodiment 1 an example in which two indoor units B and C are connected to one outdoor unit A will be described.
- the number of indoor units may be three or more, and two or more outdoor units. Machines may be connected in parallel.
- the air conditioner 100 includes an outdoor heat composed of a compressor 1, indoor heat exchangers 11b and 11c, indoor flow rate control devices 12b and 12c that are decompression devices, and parallel heat exchangers 3-1 and 3-2.
- the exchanger 3 has a main circuit which is sequentially connected by piping.
- the outdoor unit A has a compressor 1, a flow path switching device 2, an outdoor heat exchanger 3, an accumulator 4, and a backflow prevention device 5-1, 5-2, 5-3, 5-4.
- a circuit in which these are connected by piping is a part of the main circuit.
- the accumulator 4 is not necessarily essential and may be omitted.
- the flow path switching device 2 is connected between the discharge pipe 35 and the suction pipe 36 of the compressor 1 and is configured by, for example, a four-way valve that switches the flow direction of the refrigerant.
- the direction of connection is either a solid line direction or a broken line direction in FIG.
- the backflow prevention devices 5-1, 5-2, 5-3, and 5-4 are constituted by, for example, check valves that limit the flow in one direction.
- the flow direction is the direction of flow from the second extension pipe 32 to the flow path switching device 2, and no flow occurs in the reverse direction.
- the backflow prevention devices 5-1, 5-2, 5-3, and 5-4 need only be able to limit the flow in one direction, and may be configured by an opening / closing device or a throttling device having a fully closed function.
- FIG. 2 is a diagram illustrating an example of the configuration of the outdoor heat exchanger 3 of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- the outdoor heat exchanger 3 is composed of a fin tube type heat exchanger having, for example, a plurality of heat transfer tubes 3a and a plurality of fins 3b.
- the outdoor heat exchanger 3 is divided into a plurality of parallel heat exchangers.
- a configuration in which the outdoor heat exchanger 3 is divided into two parallel heat exchangers 3-1 and 3-2 is illustrated.
- the number of the parallel heat exchangers in the outdoor heat exchanger 3 is not limited to two and can be an arbitrary number.
- a plurality of heat transfer tubes 3a are provided in a row direction that is a direction perpendicular to the air passage direction and a row direction that is an air passage direction, through which the refrigerant passes.
- a plurality of fins 3b are arranged at intervals so that air passes in the air passage direction.
- the parallel heat exchangers 3-1 and 3-2 are configured by dividing the outdoor heat exchanger 3 in the casing of the outdoor unit A.
- the division may be divided into left and right, or may be divided up and down as shown in FIG.
- the refrigerant inlet to each of the parallel heat exchangers 3-1 and 3-2 is at the left and right ends of the outdoor unit A, so that the piping connection becomes complicated. There is no such thing as sticking to the exchanger.
- piping connection becomes easy.
- the fins 3b may not be divided as shown in FIG. 2, or may be divided. Also, a mechanism for reducing heat leakage is provided in the fins 3b of the parallel heat exchangers 3-1 and 3-2, or a high-temperature refrigerant is allowed to flow between the parallel heat exchangers 3-1, 3-2.
- a heat transfer tube may be provided. For example, a notch or a slit corresponds to the mechanism for reducing heat leakage provided in the fin 3b.
- the parallel functioning as an evaporator from the parallel heat exchanger to be defrosted by dividing the fins 3b, providing a mechanism for reducing heat leakage, or providing a heat transfer tube through which a high-temperature refrigerant flows.
- Heat leakage to the heat exchanger can be suppressed. If there is a heat leak, it will be difficult to defrost at the boundary between the parallel heat exchanger to be defrosted and the parallel heat exchanger functioning as an evaporator, but it will be difficult to defrost by suppressing the heat leak. Can be prevented.
- Outdoor air is transferred to the parallel heat exchangers 3-1 and 3-2 by the outdoor fan 3f.
- the outdoor fan 3 f may be installed in each of the parallel heat exchangers 3-1 and 3-2, but only one fan may be used as shown in FIG.
- First connecting pipes 37-1 and 37-2 are connected to the side of the parallel heat exchangers 3-1 and 3-2 connected to the compressor 1.
- the first connection pipes 37-1 and 37-2 are connected in parallel to a pipe 20-1 extending from the connection port on the outdoor heat exchanger 3 side of the flow path switching device 2. Opening / closing devices 6-1 and 6-2 are provided.
- Second connection pipes 38-1 and 38-2 are connected to the side of the parallel heat exchangers 3-1 and 3-2 opposite to the side connected to the compressor 1.
- the second connection pipes 38-1 and 38-2 are connected in parallel to a pipe 20-2 extending from the first extension pipe 31 toward the outdoor unit A, and each has a flow rate control device 7-1. 7-2.
- the flow control devices 7-1 and 7-2 are devices that can vary the opening degree according to a command from the control device 90, and are configured by, for example, an electronically controlled expansion valve.
- the outdoor unit A further includes a first defrost pipe 39 and a second defrost pipe 40 through which the refrigerant passes when defrosting is performed.
- the first defrost pipe 39 has one end connected to the discharge pipe 35 and the other end branched to be connected to the first connection pipes 37-1 and 37-2.
- the first defrost pipe 39 branches a part of the high-temperature and high-pressure refrigerant discharged from the compressor 1 from the main circuit and is a defrost heat exchanger that is a parallel heat exchanger 3-1 or 3-2 to be defrosted. To supply.
- One end of the second defrost pipe 40 is connected to the second connection pipe 38-2 between the parallel heat exchanger 3-1 and the flow rate control device 7-1, and the other end is connected to the parallel heat exchanger 3-2. And a second connection pipe 38-2 between the flow control device 7-2.
- the second defrost pipe 40 returns the refrigerant flowing out from the defrost heat exchanger to the main circuit.
- a first throttling device 8 is provided in the first defrost pipe 39, and a part of the high-temperature and high-pressure refrigerant discharged from the compressor 1 is decompressed to a medium pressure by the first throttling device 8.
- the medium pressure is a pressure that is lower than the high-pressure side pressure in the refrigerant circuit and higher than the low-pressure side pressure (for example, the pressure in the evaporator).
- the high pressure side pressure is, for example, the pressure in the condenser
- the low pressure side pressure is, for example, the pressure in the evaporator that absorbs heat from the outside air.
- the medium-pressure refrigerant decompressed by the first expansion device 8 flows into the parallel heat exchangers 3-1 and 3-2 through the first connection pipes 37-1 and 37-2. Thereby, defrost using the medium pressure refrigerant is performed in the parallel heat exchangers 3-1 and 3-2.
- the second branching devices 9-1 and 9-2 are provided in each of the pipes branched in the first defrost pipe 39.
- the second opening / closing devices 9-1 and 9-2 control which of the first connection pipes 37-1 and 37-2 allows the medium-pressure refrigerant to flow.
- the second opening / closing devices 9-1 and 9-2 together with the first opening / closing devices 6-1 and 6-2 constitute the “first flow path switching device” of the present invention.
- the second defrosting pipe 40 is provided with a second expansion device 10, and the refrigerant flowing out from the parallel heat exchangers 3-1 and 3-2 to be defrosted is decompressed to a low pressure.
- the first opening / closing devices 6-1 and 6-2 and the second opening / closing devices 9-1 and 9-2 are only required to be able to open and close the flow path.
- electromagnetic valves, four-way valves, three-way valves, or two It consists of a way valve.
- the second expansion device 10 is a device that can vary the opening degree according to a command from the control device 90, and is configured by, for example, an electronically controlled expansion valve.
- the first throttling device 8 may be constituted by a capillary tube as long as the necessary defrosting capacity, that is, the refrigerant flow rate for defrosting is determined. Further, even if the second opening / closing devices 9-1 and 9-2 are downsized so that the first throttle device 8 is eliminated and the preset defrost flow rate is applied to reduce the pressure from high pressure to medium pressure. good. Further, the first throttle device 8 may be eliminated, and a flow rate control device may be provided instead of the second opening / closing devices 9-1 and 9-2.
- a refrigerant pressure sensor 91 that detects the pressure of the refrigerant in the indoor heat exchanger that functions as an evaporator.
- the refrigerant pressure sensor 91 may be installed anywhere as long as it can detect the pressure of the refrigerant in the indoor heat exchanger functioning as an evaporator among the indoor heat exchangers 11b and 11c. For example, if the installation position of the refrigerant pressure sensor 91 is between the indoor heat exchangers 11b and 11c and the flow rate control devices 7-1 and 7-2, the outdoor unit A, the indoor units B and C, and the relay unit D It can be installed anywhere.
- the refrigerant pressure sensor 91 is used to detect the pressure of the portion where the refrigerant is in a gas-liquid two-phase state
- a temperature sensor that can detect the temperature of the refrigerant is used to set the detected value as the saturation temperature to the refrigerant pressure. You may convert.
- the temperature sensor may touch the refrigerant to detect the temperature of the refrigerant directly, or the temperature of the outer surface of a pipe or heat exchanger, etc. By doing so, the temperature of the refrigerant may be detected indirectly.
- a temperature sensor that can detect the air temperature is attached to the indoor unit in which the indoor heat exchanger that functions as an evaporator is installed, and the air outlet of the indoor heat exchanger that functions as an evaporator with this temperature sensor The temperature may be detected and converted to the refrigerant pressure.
- the first diaphragm device 8 in Embodiment 1 corresponds to the “first diaphragm device” of the present invention
- the second diaphragm device 10 corresponds to the “second diaphragm device” of the present invention.
- the flow rate control devices 7-1 and 7-2 correspond to the “third throttle device” and the “second flow path switching device” of the present invention, and the functions of these two devices are configured together.
- the first defrost pipe 39 corresponds to the “first defrost pipe” of the present invention
- the second defrost pipe 40 corresponds to the “second defrost pipe” of the present invention.
- the refrigerant pressure sensor 91 corresponds to the “pressure detection device” of the present invention.
- the indoor unit B and the indoor unit C have, for example, the same configuration.
- the indoor unit B includes an indoor heat exchanger 11b and an indoor flow rate control device 12b.
- the indoor unit C includes an indoor heat exchanger 11c and an indoor flow rate control device 12c.
- a circuit in which each device provided in the indoor unit B and each device provided in the indoor unit C are connected by piping is a part of the main circuit. Further, the indoor flow rate control device 12b and the indoor flow rate control device 12c correspond to the “decompression device” of the present invention.
- the indoor flow rate control devices 12b and 12c are devices that can vary the opening, and are constituted by, for example, electronically controlled expansion valves.
- the indoor flow rate control devices 12b and 12c are provided upstream of the indoor heat exchangers 11b and 11c in the refrigerant flow during the cooling only operation.
- the relay machine D includes a gas-liquid separator 13, first relay switching devices 14b and 14c, second relay switching devices 15b and 15c, a first relay flow control device 16, and a second relay flow control device. 17 and a circuit in which these are connected by piping is a part of the main circuit.
- the gas-liquid separator 13 separates the refrigerant flowing out from the first extension pipe 31 into a gas refrigerant and a liquid refrigerant.
- the gas phase part from which the gas refrigerant flows out of the gas-liquid separator 13 is connected to the third extension pipes 33b and 33c via the first relay switchgears 14b and 14c.
- the liquid phase portion from which the liquid refrigerant flows out of the gas-liquid separator 13 is connected to the second relay flow rate control device 17 and the fourth extension pipes 34b and 34c via the first relay flow rate control device 16.
- the second relay opening / closing devices 15b and 15c are provided between the second extension pipe 32 and the third extension pipes 33b and 33c, respectively.
- the second relay flow control device 17 branches from between the first relay flow control device 16 and the fourth extension pipes 34b, 34c, and the second extension pipe 32 and the second relay opening / closing devices 15b, 15c. It is provided in the pipe connected between.
- the first relay opening / closing devices 14b and 14c and the second relay opening / closing devices 15b and 15c may be electromagnetic valves, four-way valves, three-way valves, two-way valves, or the like as long as the flow paths can be opened and closed.
- the first relay flow control device 16 and the second relay flow control device 17 are devices that can vary the opening degree, and are configured by, for example, an electronically controlled expansion valve.
- the first relay switchgears 14b and 14c and the second relay switchgears 15b and 15c in Embodiment 1 correspond to the “connection switching device” of the present invention.
- the operation of the air conditioner 100 includes a cooling only operation in which the outdoor heat exchanger 3 functions as a condenser, a cooling main operation, a heating operation in which the outdoor heat exchanger 3 functions as an evaporator, and a heating main operation.
- the all heating operation is an operation in which all indoor units in operation only perform heating.
- the all-cooling operation is an operation in which all indoor units that are in operation only perform cooling.
- Cooling-dominated operation or heating-dominated operation is a simultaneous cooling / heating operation in which both indoor units that are heating and indoor units that are performing cooling are mixed, and cooling-dominated operation is performed when the cooling load is greater than the heating load.
- the heating main operation is performed when the heating load is greater than the cooling load.
- the cooling load and the heating load are the pressure of the refrigerant discharged from the compressor 1, the pressure of the refrigerant sucked into the compressor 1, the capacity of the operating indoor unit, the number of units operated, and the temperature difference between the indoor set temperature and the indoor temperature. You can know by detecting. Such information for knowing the cooling load and the heating load can be obtained by the control device 90.
- the heating normal operation in which both the parallel heat exchangers 3-1 and 3-2 constituting the outdoor heat exchanger 3 function as an evaporator, and the parallel heat exchangers 3-1 and 3-
- a heating only defrosting operation also called continuous heating only operation
- the heating main operation further includes a heating main normal operation in which both of the parallel heat exchangers 3-1 and 3-2 constituting the outdoor heat exchanger 3 function as an evaporator, a parallel heat exchanger 3-1
- There is a heating main defrost operation also referred to as continuous heating main operation in which one of 3-2 functions as an evaporator.
- the heating main defrost operation corresponds to the “first operation” of the present invention
- the heating main normal operation corresponds to the “second operation” of the present invention.
- the parallel heat exchanger 3-1 and the parallel heat exchanger 3-2 are alternately defrosted while heating is continued. That is, defrosting of the other parallel heat exchanger is performed while heating with one parallel heat exchanger functioning as an evaporator.
- the other parallel heat exchanger is caused to function as an evaporator to perform heating, and the defrosting of the one parallel heat exchanger is performed.
- FIG. 3 is a diagram showing the states of the opening / closing devices, the flow rate control device, and the expansion device in each operation mode of the outdoor unit A of FIG.
- FIG. 4 is a diagram illustrating a state of each flow control device in the indoor units B and C in FIG. 1.
- FIG. 5 is a diagram illustrating the states of the switching devices and the flow rate control device in each operation mode of the relay machine D in FIG. 1.
- ON of the flow path switching device 2 indicates a case where it is connected in the direction of the solid line in FIG. 1
- OFF indicates a case where it is connected in the direction of the dotted line.
- the first switchgears 6-1 and 6-2 and the second switchgears 9-1 and 9-2 in FIG. 3 are turned ON, and the first relay switchgears 14b and 14c and the second relay switchgear in FIG. ON of the devices 15b and 15c indicates a case where the opening / closing device is open and the refrigerant flows, and OFF indicates a case where the opening / closing device is closed.
- FIG. 6 is a diagram showing the refrigerant flow during the cooling only operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- a portion where the refrigerant flows during the cooling only operation is a solid line, and a portion where the refrigerant does not flow is a broken line.
- FIG. 6 shows a case where the indoor units B and C are performing cooling.
- FIG. 7 is a Ph diagram during the cooling operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Note that the points (a) to (f) in FIG. 7 indicate the state of the refrigerant in the portions marked with the same symbols in FIG.
- the low-temperature and low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature and high-pressure gas refrigerant.
- the refrigerant compression process of the compressor 1 is compressed so as to be heated by an amount equivalent to the adiabatic efficiency of the compressor 1 as compared with the case of adiabatic compression with an isentropic line, and the point from point (a) in FIG. It is represented by the line shown in (b).
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and is branched into two, one of which passes through the first opening / closing device 6-1 and the first connection pipe 37- 1 flows into the parallel heat exchanger 3-1.
- the other passes through the first switch 6-2 and flows into the parallel heat exchanger 3-2 from the first connection pipe 37-2.
- the refrigerant flowing into the parallel heat exchangers 3-1 and 3-2 is cooled while heating the outdoor air, and becomes a medium-temperature and high-pressure liquid refrigerant.
- the refrigerant change in the parallel heat exchangers 3-1 and 3-2 is represented by a slightly inclined straight line that is slightly inclined from the point (b) to the point (c) in FIG.
- the merged refrigerant passes through the backflow prevention device 5-1, passes through the first extension pipe 31, and flows into the repeater D.
- either one of the first switchgears 6-1 and 6-2 is closed, and either of the parallel heat exchangers 3-1 or 3-2 is closed.
- the refrigerant may be prevented from flowing to one side. In this case, as a result, the heat transfer area of the outdoor heat exchanger 3 is reduced, and a stable cycle operation can be performed.
- the refrigerant that has flowed into the relay unit D flows into the gas-liquid separator 13.
- the gas-liquid separator 13 separates the inflowing refrigerant into gas refrigerant and liquid refrigerant.
- the inflowing refrigerant here is liquid refrigerant, and the first relay opening / closing devices 14b and 14c are closed. Therefore, all the inflowing liquid refrigerant flows out from the liquid phase part.
- the liquid refrigerant that has flowed out of the gas-liquid separator 13 passes through the fully opened first relay flow controller 16 and is branched into two, one of which passes through the fourth extension pipes 34b and 34c and performs cooling. Flows into the existing indoor units B and C. The other flows into the second relay flow rate control device 17, where it is throttled and expanded and depressurized to become a low-temperature low-pressure gas-liquid two-phase refrigerant.
- the change of the refrigerant in the second relay flow rate control device 17 is performed under a constant enthalpy.
- the refrigerant change at this time is represented by the vertical line shown from the point (c) to the point (f) in FIG.
- the liquid refrigerant that has flowed into the indoor units B and C flows into the indoor flow rate control devices 12b and 12c, where they are throttled and expanded and depressurized to be in a low-temperature and low-pressure gas-liquid two-phase state.
- the change of the refrigerant in the indoor flow rate control devices 12b and 12c is performed under a constant enthalpy.
- the refrigerant change at this time is represented by the vertical line shown from the point (c) to the point (d) in FIG.
- the low-temperature and low-pressure gas-liquid two-phase refrigerant that has flowed out of the indoor flow rate control devices 12b and 12c flows into the indoor heat exchangers 11b and 11c functioning as an evaporator.
- the refrigerant flowing into the indoor heat exchangers 11b and 11c is heated while cooling the indoor air, and becomes a low-temperature and low-pressure gas refrigerant.
- the indoor flow rate controllers 12b and 12c are controlled so that the degree of superheat (superheat) of the low-temperature and low-pressure gas refrigerant flowing out from the indoor heat exchangers 11b and 11c is about 2K to 5K. Changes in the refrigerant in the indoor heat exchangers 11b and 11c are expressed by a slightly inclined straight line that is slightly inclined from the point (d) to the point (e) in FIG.
- the low-temperature and low-pressure gas refrigerants flowing out from the indoor heat exchangers 11b and 11c flow into the relay D again through the third extension pipes 33b and 33c.
- the low-temperature and low-pressure gas refrigerant that has flowed into the relay D again passes through the second relay opening / closing devices 15b and 15c, and then passes through the second relay flow rate control device 17 in a low-temperature and low-pressure gas-liquid two-phase state. And flows into the outdoor unit A through the second extension pipe 32.
- the low-temperature and low-pressure gas refrigerant that has passed through the indoor units B and C has a higher flow rate than the low-temperature and low-pressure gas-liquid two-phase refrigerant that has passed through the second relay flow control device 17.
- the low-temperature and low-pressure gas refrigerant flowing into the outdoor unit A flows into the compressor 1 through the backflow prevention device 5-2, the flow path switching device 2, and the accumulator 4, and is compressed.
- FIG. 8 is a diagram showing the refrigerant flow during the cooling main operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- a portion where the refrigerant flows during the cooling main operation is a solid line, and a portion where the refrigerant does not flow is a broken line.
- FIG. 8 shows a case where the indoor unit B is cooling and the indoor unit C is heating. Similarly, in the following description of the embodiments, the case where the indoor unit B is cooling and the indoor unit C is heating will be described.
- the indoor unit B When the indoor unit B performs heating and the indoor unit C performs cooling, the open / close states of the indoor flow rate control devices 12b and 12c, the first relay switching devices 14b and 14c, and the second relay switching devices 15b and 15c are reversed, The other operations are the same only by switching the refrigerant flows in the indoor unit B and the indoor unit C.
- FIG. 9 is a Ph diagram during the cooling main operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Note that the points (a) to (j) in FIG. 9 indicate the state of the refrigerant in the portion with the same symbol in FIG.
- the low-temperature and low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature and high-pressure gas refrigerant.
- the refrigerant compression process of the compressor 1 is compressed so as to be heated by an amount equivalent to the adiabatic efficiency of the compressor 1 as compared with the case of adiabatic compression with an isentropic line. It is represented by the line shown in (b).
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and is branched into two, one of which passes through the first opening / closing device 6-1 and the first connection pipe 37- 1 flows into the parallel heat exchanger 3-1.
- the other passes through the first switch 6-2 and flows into the parallel heat exchanger 3-2 from the first connection pipe 37-2.
- the refrigerant flowing into the parallel heat exchangers 3-1 and 3-2 is cooled while heating the outdoor air, and becomes a medium-temperature and high-pressure gas-liquid two-phase refrigerant.
- the refrigerant change in the parallel heat exchangers 3-1 and 3-2 is represented by a slightly inclined straight line that is slightly inclined from the point (b) to the point (c) in FIG. 9 in consideration of the pressure loss.
- either the first switchgear 6-1 or 6-2 is closed.
- the refrigerant may be prevented from flowing into either one of the parallel heat exchangers 3-1, 3-2.
- the heat transfer area of the outdoor heat exchanger 3 is reduced, and a stable cycle operation can be performed.
- the refrigerant that has flowed into the relay unit D flows into the gas-liquid separator 13.
- the gas refrigerant is separated into the liquid refrigerant
- the gas refrigerant flows out from the gas phase portion and flows into the first relay opening / closing device 14c
- the liquid refrigerant flows out from the liquid phase portion to the first phase. It flows into the relay flow rate control device 16.
- the refrigerant change in the gas-liquid separator 13 is performed under a constant pressure, and is separated into a saturated gas and a saturated liquid.
- the gas refrigerant flowing out from the gas phase portion is represented by a horizontal line shown from point (c) to point (g) in FIG. 9, and the liquid refrigerant flowing out from the liquid phase portion is point (i) from point (c) in FIG. It is represented by the horizontal line shown in
- the gas refrigerant that has flowed into the first relay opening / closing device 14c flows into the indoor unit C that is heating through the third extension pipe 33c.
- the gas refrigerant flowing into the indoor unit C flows into the indoor heat exchanger 11c functioning as a condenser, where it is cooled while heating the indoor air, and becomes a medium-temperature and high-pressure liquid refrigerant.
- the change of the refrigerant in the indoor heat exchanger 11c is represented by a slightly inclined horizontal line shown from the point (g) to the point (h) in FIG.
- the medium-temperature and high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 11c flows into the indoor flow rate control device 12c, where it is squeezed and expanded and depressurized, and then flows out of the indoor unit C and passes through the fourth extension pipe 34c. To do.
- the indoor flow rate control device 12c is controlled so that the subcooling degree of the medium temperature and high pressure liquid refrigerant flowing out of the indoor heat exchanger 11c is about 5K to 20K.
- the liquid refrigerant that has flowed into the first relay flow control device 16 is squeezed here to expand and depressurize.
- the change of the refrigerant in the first relay flow control device 16 is performed under a constant enthalpy.
- the refrigerant change at this time is represented by the vertical line shown from the point (i) to the point (j) in FIG.
- the refrigerant that has flowed out of the first relay flow control device 16 is branched into two, and one of the refrigerant flows out of the indoor unit C and merges with the refrigerant that has passed through the fourth extension pipe 34c, and the fourth extension pipe 34b. And flows into the indoor unit B that is performing cooling.
- the other flows into the second relay flow rate control device 17, where it is throttled and expanded and depressurized to enter a low-temperature and low-pressure gas-liquid two-phase state.
- the change of the refrigerant in the second relay flow rate control device 17 is performed under a constant enthalpy.
- the refrigerant change at this time is represented by the vertical line shown from the point (j) to the point (f) in FIG.
- the refrigerant that merges and flows into the indoor unit B depends on the magnitude relationship between the flow rate of the refrigerant passing through the indoor unit C and the flow rate of the refrigerant passing through the first relay flow control device 16 and the heating load of the indoor unit C. It becomes a liquid refrigerant or a gas-liquid two-phase refrigerant.
- the change of the refrigerant in the indoor flow control device 12b is performed under a constant enthalpy, and the state of the refrigerant flowing out of the indoor flow control device 12b is represented by a point (d) in FIG.
- the low-temperature low-pressure gas-liquid two-phase refrigerant that has flowed out of the indoor flow rate control device 12b flows into the indoor heat exchanger 11b that functions as an evaporator.
- the refrigerant flowing into the indoor heat exchanger 11b is heated while cooling the indoor air, and becomes a low-temperature and low-pressure gas refrigerant.
- the indoor flow rate control device 12b is controlled so that the degree of superheat (superheat) of the low-temperature and low-pressure gas refrigerant flowing out from the indoor heat exchanger 11b is about 2K to 5K.
- the change of the refrigerant in the indoor heat exchanger 11b is represented by a slightly inclined horizontal line shown from the point (d) to the point (e) in FIG.
- the low-temperature and low-pressure gas refrigerant that has flowed out of the indoor heat exchanger 11b flows into the repeater D again through the third extension pipe 33b.
- the low-temperature and low-pressure gas refrigerant that has flowed into the relay unit D again passes through the second relay opening / closing device 15b, and then merges with the low-temperature and low-pressure two-phase refrigerant that has passed through the second relay flow control device 17 to the second relay switch D. It flows into the outdoor unit A through the extension pipe 32.
- the low-temperature and low-pressure gas refrigerant that has passed through the indoor units B and C has a higher flow rate than the low-temperature and low-pressure two-phase refrigerant that has passed through the second relay flow rate control device 17, and merges into the outdoor unit A.
- the refrigerant flowing in is a low-temperature and low-pressure gas refrigerant with a small degree of superheat, and the state of the refrigerant is point (a) in FIG.
- the low-temperature and low-pressure gas refrigerant flowing into the outdoor unit A flows into the compressor 1 through the backflow prevention device 5-2, the flow path switching device 2, and the accumulator 4, and is compressed.
- FIG. 10 is a diagram illustrating a refrigerant flow during the normal heating normal operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- coolant flows at the time of heating only normal operation is made into the continuous line, and the part into which a refrigerant
- the case where the indoor units B and C are heating is shown.
- FIG. 11 is a Ph diagram during normal heating operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Note that the points (a) to (d) in FIG. 11 indicate the state of the refrigerant in the portion with the same symbol in FIG.
- the low-temperature and low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature and high-pressure gas refrigerant.
- the refrigerant compression process of the compressor 1 is compressed so as to be heated by an amount equivalent to the adiabatic efficiency of the compressor 1 as compared with the case of adiabatic compression with an isentropic line, and from the point (a) in FIG. It is represented by the line shown in (b).
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and then flows out of the outdoor unit A through the backflow prevention device 5-3.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit A passes through the first extension pipe 31 and flows into the relay unit D.
- the refrigerant that has flowed into the relay unit D flows into the gas-liquid separator 13.
- the gas-liquid separator 13 separates the inflowing refrigerant into a gas refrigerant and a liquid refrigerant.
- the inflowing refrigerant is a gas refrigerant and the first relay flow rate control device 16 is closed, All the gas refrigerant that has flowed in flows out of the gas phase.
- the gas refrigerant flowing out of the gas-liquid separator 13 passes through the first relay opening / closing devices 14b and 14c, passes through the third extension pipes 33b and 33c, and flows into the indoor units B and C that are heating.
- the refrigerant that has flowed into the indoor units B and C flows into the indoor heat exchangers 11b and 11c functioning as condensers, and is cooled while heating the indoor air, and becomes a medium-temperature and high-pressure liquid refrigerant.
- the change of the refrigerant in the indoor heat exchangers 11b and 11c is represented by a slightly inclined straight line that is slightly inclined from the point (b) to the point (c) in FIG.
- the medium-temperature and high-pressure liquid refrigerant that has flowed out of the indoor heat exchangers 11b and 11c flows into the indoor flow rate control devices 12b and 12c, where they are throttled and expanded and depressurized.
- the change of the refrigerant in the indoor flow rate control devices 12b and 12c is performed under a constant enthalpy.
- the indoor flow rate control devices 12b and 12c are controlled so that the degree of subcooling of the medium-temperature and high-pressure liquid refrigerant is about 5K to 20K.
- the refrigerant that has flowed out of the indoor flow rate control devices 12b and 12c flows into the repeater D again through the fourth extension pipes 34b and 34c.
- the refrigerant that has flowed into the relay unit D again passes through the second relay flow rate control device 17 in the fully open state, and then flows into the outdoor unit A through the second extension pipe 32.
- the refrigerant flowing into the outdoor unit A passes through the backflow prevention device 5-4 and flows into the second connection pipes 38-1 and 38-2.
- the refrigerant flowing into the second connection pipes 38-1 and 38-2 is throttled by the flow rate control devices 7-1 and 7-2, and is expanded and depressurized to be in a low-pressure gas-liquid two-phase state.
- the change of the refrigerant in the flow rate control devices 7-1 and 7-2 is performed under a constant enthalpy. Since the change of the refrigerant from the indoor heat exchangers 11b and 11c through the flow rate control devices 7-1 and 7-2 is performed under a constant enthalpy, the change of the refrigerant is indicated by the point (c ) To point (d).
- the flow rate control devices 7-1 and 7-2 are fixed at a constant opening, for example, fully open, or the saturation temperature of the intermediate pressure such as the second extension pipe 32 detected by the refrigerant pressure sensor 91 is maintained.
- the temperature may be controlled to be about 0 ° C to 20 ° C. By controlling the saturation temperature of the intermediate pressure of the second extension pipe 32 or the like, condensation or icing on the pipe surface can be prevented.
- the refrigerant that has flowed out of the flow control devices 7-1 and 7-2 flows into the parallel heat exchangers 3-1 and 3-2, and is heated while cooling the outdoor air to become a low-temperature and low-pressure gas refrigerant.
- the refrigerant change in the parallel heat exchangers 3-1 and 3-2 is represented by a slightly inclined straight line that is slightly inclined from the point (d) to the point (a) in FIG. 11 in consideration of the pressure loss.
- the low-temperature and low-pressure gas refrigerant that has flowed out of the parallel heat exchangers 3-1 and 3-2 flows into the first connection pipes 37-1 and 37-2, and passes through the first switchgears 6-1 and 6-2. After passing, they merge, pass through the flow path switching device 2 and the accumulator 4, flow into the compressor 1, and are compressed.
- FIG. 12 is a diagram showing the refrigerant flow during the heating-main normal operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
- the portion where the refrigerant flows during the heating-main normal operation is indicated by a solid line, and the portion where the refrigerant does not flow is indicated by a broken line.
- FIG. 12 shows a case where the indoor unit B is cooling and the indoor unit C is heating.
- the indoor unit B When the indoor unit B performs heating and the indoor unit C performs cooling, the open / close states of the indoor flow rate control devices 12b and 12c, the first relay switching devices 14b and 14c, and the second relay switching devices 15b and 15c are reversed, The other operations are the same only by switching the refrigerant flows in the indoor unit B and the indoor unit C.
- FIG. 13 is a Ph diagram during normal heating operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Note that the points (a) to (h) in FIG. 13 indicate the state of the refrigerant in the portions marked with the same symbols in FIG.
- the low-temperature and low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature and high-pressure gas refrigerant.
- the refrigerant compression process of the compressor 1 is compressed so as to be heated by an amount equivalent to the heat insulation efficiency of the compressor 1 as compared with the case of adiabatic compression with an isentropic line, and the point from point (a) in FIG. It is represented by the line shown in (b).
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switching device 2 and then flows out of the outdoor unit A through the backflow prevention device 5-3.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit A passes through the first extension pipe 31 and flows into the relay unit D.
- the refrigerant that has flowed into the relay unit D flows into the gas-liquid separator 13.
- the gas-liquid separator 13 separates the inflowing refrigerant into a gas refrigerant and a liquid refrigerant.
- the inflowing refrigerant is a gas refrigerant and the first relay flow rate control device 16 is closed, All the gas refrigerant that has flowed in flows out of the gas phase.
- the gas refrigerant that has flowed out of the gas-liquid separator 13 passes through the first relay opening / closing device 14c, passes through the third extension pipe 33c, and flows into the indoor unit C that performs heating.
- the refrigerant that has flowed into the indoor unit C flows into the indoor heat exchanger 11c functioning as a condenser, is cooled while heating the indoor air, and becomes a medium-temperature and high-pressure liquid refrigerant.
- the change of the refrigerant in the indoor heat exchanger 11c is represented by a slightly inclined horizontal line as shown in FIG. 13 from the point (b) to the point (c) in consideration of the pressure loss.
- the change of the refrigerant in the indoor flow control device 12c is performed under a constant enthalpy.
- the indoor flow control device 12c is controlled so that the degree of subcooling of the medium-temperature and high-pressure liquid refrigerant is about 5K to 20K.
- the refrigerant that has flowed out of the indoor flow rate control device 12c is branched into two through the fourth extension pipe 34c, one flows again into the relay unit D, and the other is cooled through the fourth extension pipe 34b. Flows into the indoor unit B.
- the refrigerant that has flowed again into the relay unit D passes through the second relay flow rate control device 17 and is reduced to an intermediate pressure, and then flows into the outdoor unit A through the second extension pipe 32.
- the change of the refrigerant in the second relay flow rate control device 17 is performed under a constant enthalpy. Since the change of the refrigerant from the indoor heat exchanger 11c through the second relay flow rate control device 17 is performed under a constant enthalpy, the change of the refrigerant is changed from the point (c) in FIG. e). Note that the second relay flow rate control device 17 is controlled so as to adjust the flow rate of refrigerant passing therethrough and the pressure difference between the front and rear.
- the refrigerant that has flowed into the indoor unit B flows into the indoor flow rate control device 12b, where it is throttled and expanded and depressurized to be in a gas-liquid two-phase state with an intermediate temperature and intermediate pressure.
- the change of the refrigerant in the indoor flow rate control device 12b is performed under a constant enthalpy. Since the change of the refrigerant from the indoor heat exchanger 11c through the indoor flow rate control device 12b is performed under a constant enthalpy, the change of the refrigerant is changed from the point (c) to the point (f) in FIG. Become.
- the medium-temperature intermediate-pressure gas-liquid refrigerant that has flowed out of the indoor flow rate control device 12b flows into the indoor heat exchanger 11b functioning as an evaporator.
- the refrigerant that has flowed into the indoor heat exchanger 11b is heated while cooling the room air, and becomes a gas refrigerant having an intermediate temperature and intermediate pressure.
- the indoor flow rate control device 12b is controlled so that the superheat of the medium temperature intermediate pressure gas refrigerant flowing out of the indoor heat exchanger 11b is about 2K to 5K.
- the change of the refrigerant in the indoor heat exchanger 11b is represented by a slightly inclined horizontal line shown from the point (f) to the point (g) in FIG.
- the medium-temperature intermediate-pressure gas refrigerant that has flowed into the relay machine D again through the indoor unit B passes through the second relay opening / closing device 15b, and then merges with the refrigerant that has passed through the second relay flow control device 17. It flows into the outdoor unit A through the second extension pipe 32.
- the refrigerant that joins and flows into the outdoor unit A becomes a liquid refrigerant of intermediate temperature / intermediate pressure or a gas-liquid two-phase refrigerant according to the operation load of the indoor units B and C, and is indicated by a point (h) in FIG.
- the refrigerant flowing into the outdoor unit A passes through the backflow prevention device 5-4 and flows into the second connection pipes 38-1 and 38-2.
- the refrigerant flowing into the second connection pipes 38-1 and 38-2 is throttled by the flow rate control devices 7-1 and 7-2, and is expanded and depressurized to be in a low-pressure gas-liquid two-phase state.
- the change of the refrigerant in the flow rate control devices 7-1 and 7-2 is performed under a constant enthalpy.
- the change of the refrigerant at this time is changed from the point (h) to the point (d) in FIG.
- the detected pressure of the refrigerant pressure sensor 91 is the pressure of the refrigerant of the indoor heat exchanger 11b functioning as an evaporator, and the saturation conversion temperature of this detected pressure corresponds to the refrigerant temperature of the indoor heat exchanger 11b.
- the flow rate control devices 7-1 and 7-2 are configured so that the refrigerant temperature of the indoor heat exchanger 11b functioning as an evaporator becomes a target temperature according to the set temperature of the indoor unit B that is performing cooling. Be controlled.
- the flow rate control devices 7-1 and 7-2 control the detected pressure of the refrigerant pressure sensor 91 to be a target pressure corresponding to the set temperature of the indoor unit B that is performing cooling. Is done.
- the saturation temperature of the refrigerant in the indoor heat exchanger 11b can be adjusted by controlling the pressure of the indoor heat exchanger 11b that performs cooling, the temperature of the air that is cooled by exchanging heat with the refrigerant in the indoor heat exchanger 11b is adjusted. Can be adjusted.
- the indoor unit B that performs cooling can be operated in accordance with the indoor set temperature and cooling load, and indoor comfort can be improved. it can.
- the target pressure of the refrigerant pressure of the indoor heat exchanger 11b is set to a temperature not lower than 0 ° C. and not higher than a set temperature in terms of saturation temperature. That is, by setting the refrigerant temperature of the indoor heat exchanger 11b to 0 ° C. or higher, frost formation and freezing in the indoor heat exchanger 11b functioning as an evaporator can be prevented. In addition, by setting the refrigerant temperature of the indoor heat exchanger 11b to be equal to or lower than the set temperature, the indoor temperature can be set to the set temperature, and indoor comfort can be improved.
- the refrigerant that has flowed out of the flow control devices 7-1 and 7-2 flows into the parallel heat exchangers 3-1 and 3-2, and is heated while cooling the outdoor air to become a low-temperature and low-pressure gas refrigerant.
- the refrigerant change in the parallel heat exchangers 3-1 and 3-2 is represented by a slightly inclined straight line that is slightly inclined from the point (d) to the point (a) in FIG.
- the low-temperature and low-pressure gas refrigerant that has flowed out of the parallel heat exchangers 3-1 and 3-2 flows into the first connection pipes 37-1 and 37-2, and passes through the first switchgears 6-1 and 6-2. After passing, they merge, pass through the flow path switching device 2 and the accumulator 4, flow into the compressor 1, and are compressed.
- the all-heating defrost operation is performed when the outdoor heat exchanger 3 is frosted during the all-heating normal operation. Alternatively, when the indoor unit that performs cooling is stopped during the heating-based defrosting operation and all the indoor units that are operating are heated, the heating only defrosting operation is performed.
- the determination of the presence or absence of frost formation is performed when, for example, the saturation temperature converted from the suction pressure of the compressor 1 is significantly lower than the preset outside air temperature.
- the temperature difference between the outside air temperature and the saturation temperature converted from the suction pressure is equal to or greater than a preset value, and frost formation is determined when the elapsed time exceeds a certain time.
- the parallel heat exchanger 3-2 in the heating only defrost operation, the parallel heat exchanger 3-2 is defrosted, and the parallel heat exchanger 3-1 functions as an evaporator to perform heating. If you have driving. Conversely, there is an operation in the case where the parallel heat exchanger 3-2 functions as an evaporator to continue heating and defrost the parallel heat exchanger 3-1.
- FIG. 14 is a diagram showing the refrigerant flow during the heating only defrost operation in which the defrost of the parallel heat exchanger 3-2 of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention is performed.
- a portion where the refrigerant flows during the heating-only defrost operation is a solid line, and a portion where the refrigerant does not flow is a broken line.
- FIG. 15 is a Ph diagram at the time of the heating only defrost operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Note that the points (a) to (e), the point (k), and the point (l) in FIG. 15 indicate the state of the refrigerant in the portion denoted by the same symbol in FIG.
- the controller 90 detects that the defrost that eliminates the frosting state is necessary during the heating only normal operation shown in FIG. 10, the first control unit 90 corresponding to the parallel heat exchanger 3-2 to be defrosted.
- the opening / closing device 6-2 is closed, and the flow control device 7-2 is closed.
- the second opening / closing device 9-2 is opened, the opening of the first expansion device 8 is opened to a preset initial opening, and the opening of the second expansion device 10 is opened to a preset initial opening.
- the first switch 6-1 corresponding to the parallel heat exchanger 3-1 functioning as an evaporator is opened, and the second switch 9-1 is closed.
- the refrigerant depressurized to the medium pressure (point (k)) passes through the second switch 9-2 and flows into the parallel heat exchanger 3-2.
- the refrigerant flowing into the parallel heat exchanger 3-2 is cooled by exchanging heat with the frost attached to the parallel heat exchanger 3-2.
- the frost adhering to the parallel heat exchanger 3-2 can be melted by flowing the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 into the parallel heat exchanger 3-2.
- the change of the refrigerant at this time is represented by the change from the point (k) to the point (l) in FIG.
- the parallel heat exchanger 3-2 to be defrosted defrosts using latent heat that does not accompany the temperature change of the refrigerant.
- the refrigerant for defrosting has a saturation temperature of about 0 ° C. to 10 ° C. above the frost temperature (0 ° C.).
- the refrigerant that has been defrosted and flows out of the parallel heat exchanger 3-2 flows into the second defrost pipe 40, is depressurized to a low pressure by the second expansion device 10, and joins the main circuit.
- the merged refrigerant flows into the parallel heat exchanger 3-1 functioning as an evaporator and evaporates.
- the control device 90 sets the opening of the second expansion device 10 and the refrigerant pressure of the parallel heat exchanger 3-2 to be defrosted is about 0 ° C. to 10 ° C. in terms of saturation temperature. To control. Further, during the heating only defrost operation, the difference between the discharge pressure of the compressor 1 and the pressure of the parallel heat exchanger 3-2 to be defrosted does not change greatly, so the opening degree of the first expansion device 8 is set in advance. Keep the opening fixed to match the required defrost flow designed.
- the opening degree of the second expansion device 10 is controlled so that the refrigerant temperature (saturation temperature) of the parallel heat exchanger 3-2 to be defrosted is about 0 ° C. to 10 ° C.
- the refrigerant temperature of the parallel heat exchanger 3-2 to be defrosted is less than 0 ° C.
- the refrigerant temperature is lower than the frost temperature (0 ° C.).
- Defrosting is performed using only heat.
- the flow rate of the refrigerant flowing into the parallel heat exchanger 3-2 is increased, the flow rate of the refrigerant used for heating is reduced correspondingly, so that the heating capacity is reduced and indoor comfort is reduced.
- the refrigerant temperature of the parallel heat exchanger 3-2 to be defrosted is higher than 10 ° C, the temperature difference from the frost temperature (0 ° C) is large, and the refrigerant flowing into the parallel heat exchanger 3-2 Since the liquid is immediately liquefied, the amount of liquid refrigerant existing in the parallel heat exchanger 3-2 increases. Also in this case, since the amount of refrigerant used for heating is insufficient, the heating capacity is reduced, and the indoor comfort is reduced.
- the opening degree of the second expansion device 10 is controlled so that the refrigerant temperature of the parallel heat exchanger 3-2 is about 0 ° C. to 10 ° C.
- the defrost has a large amount of heat.
- Sufficient refrigerant can be supplied for heating while using latent heat. Therefore, heating capability can be ensured and indoor comfort can be improved.
- the controller 90 may control the opening degree of the first expansion device 8 and the second expansion device 10 so that the refrigerant flow rate used for defrost increases as the outside air temperature decreases.
- the amount of heat given to the frost can be made constant regardless of the outside air temperature, and the time taken for defrosting can be made constant.
- control device 90 may change the threshold value of the saturation temperature and the normal operation time used when determining the presence or absence of frosting according to the outside air temperature. For example, the duration of the heating operation may be shortened as the outside air temperature decreases. If the duration of heating operation is shortened, the amount of frost formation at the start of defrosting is reduced.
- the amount of heat applied to the defrost by the refrigerant during the defrost is constant regardless of the outside air temperature, the amount of frost that can be removed decreases as the outside air temperature decreases. For this reason, in order to remove frost attached during heating operation with a constant amount of heat regardless of the outside air temperature, the duration of heating operation is shortened as the outside air temperature decreases, and the amount of frost formation at the start of defrosting is reduced. Good.
- the amount of heat applied to the defrost by the refrigerant during the defrost can be made constant regardless of the outside air temperature.
- the structure of the first expansion device 8 can be simplified. That is, since the resistance of the first expansion device 8 can be made constant, an inexpensive capillary tube can be used for the first expansion device 8. The point that the threshold value of the saturation temperature and the normal operation time used when determining the presence or absence of frost formation may be changed according to the outside air temperature is the same in the heating main defrost operation described later.
- the parallel heat exchangers 3-1 and 3-2 are integrated, and the outdoor air from the outdoor fan 3f is also conveyed to the parallel heat exchanger to be defrosted.
- the fan output may be changed according to the outside air temperature. Specifically, the fan output may be decreased as the outside air temperature decreases.
- the defrost can be terminated quickly. Also, if the heating capacity of the defrost is lowered by the amount of the reduced heat release, the heating capacity can be increased accordingly.
- control device 90 may provide a threshold temperature for the outside air temperature and switch the defrost operation according to the magnitude relationship between the outside air temperature and the threshold temperature. Specifically, when the outside air temperature is higher than the threshold temperature, the heating only defrost operation is performed. On the other hand, when the outside air temperature is equal to or lower than the threshold temperature, the connection of the flow path switching device 2 is switched in the same direction as in the cooling operation, and the refrigerant flows in the all cooling operation, so-called reverse defrost operation is performed.
- the threshold temperature is, for example, ⁇ 5 ° C. or ⁇ 10 ° C.
- the amount of heat released from the outdoor heat exchanger 3 to be defrosted to the outside air increases.
- the all-heating defrost operation is performed, and when the outside air temperature is equal to or lower than the threshold temperature, the reverse defrost operation is performed, whereby the defrost can be efficiently performed.
- the heating main defrost operation is performed when the outdoor heat exchanger 3 is frosted during the heating main normal operation. Alternatively, the heating main defrost operation is also performed when cooling is started in a part of the indoor unit during the all heating defrost operation.
- the parallel heat exchanger 3-2 performs defrosting and the parallel heat exchanger 3-1 functions as an evaporator and continues heating, as in the all-heating defrost operation.
- the indoor unit B performs cooling and the indoor unit C performs heating as in the heating-main normal operation will be described.
- FIG. 16 is a diagram showing a refrigerant flow during a heating main defrost operation in which the defrost of the parallel heat exchanger 3-2 of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention is performed.
- a portion where the refrigerant flows during the heating main defrost operation is a solid line, and a portion where the refrigerant does not flow is a broken line.
- FIG. 17 is a Ph diagram at the time of heating main defrost operation of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Note that the points (a) to (h), the point (k), and the point (l) in FIG. 17 indicate the state of the refrigerant in the portion denoted by the same symbol in FIG.
- the controller 90 When the controller 90 detects that the defrost that eliminates the frost state is necessary during the heating-main normal operation shown in FIG. 12, the controller 90 performs the first operation corresponding to the parallel heat exchanger 3-2 to be defrosted.
- the opening / closing device 6-2 is closed, and the flow control device 7-2 is closed.
- the second opening / closing device 9-2 is opened, the opening of the first expansion device 8 is opened to a preset initial opening, and the opening of the second expansion device 10 is opened to a preset initial opening.
- the first switch 6-1 corresponding to the parallel heat exchanger 3-1 functioning as an evaporator is opened, and the second switch 9-1 is closed.
- the refrigerant depressurized to the medium pressure (point (k)) passes through the second switch 9-2 and flows into the parallel heat exchanger 3-2.
- the refrigerant flowing into the parallel heat exchanger 3-2 is cooled by exchanging heat with the frost attached to the parallel heat exchanger 3-2.
- the change of the refrigerant at this time is represented by the change from the point (k) to the point (l) in FIG.
- the refrigerant for defrosting has a saturation temperature of about 0 ° C. to 10 ° C. above the frost temperature (0 ° C.).
- the refrigerant that has been defrosted and flows out of the parallel heat exchanger 3-2 flows into the second defrost pipe 40, is depressurized to a low pressure by the second expansion device 10, and joins the main circuit.
- the change of the refrigerant at this time is represented by the point (d) from the point (l) in FIG.
- the refrigerant joined to the main circuit flows into the parallel heat exchanger 3-1 functioning as an evaporator and evaporates.
- the change of the refrigerant at this time is represented by the point (a) from the point (d) in FIG.
- the control device 90 sets the opening degree of the second expansion device 10 and the refrigerant pressure of the parallel heat exchanger 3-2 to be defrosted is about 0 ° C. to 10 ° C. at the saturation conversion temperature. To control. Moreover, the opening degree of the 1st expansion device 8 is kept fixed according to the required defrost flow volume designed beforehand. Alternatively, the control device 90 may control the first expansion device 8 and the second expansion device 10 so that the defrost flow rate increases as the outside air temperature decreases.
- the control device 90 determines the opening degree of the flow rate control device 7-1 based on the detected pressure of the refrigerant pressure sensor 91, that is, the refrigerant pressure of the indoor heat exchanger 11b functioning as an evaporator. It controls so that it may become the target pressure according to preset temperature etc. of the indoor unit B which is performing.
- the flow rate control device 7-1 is provided upstream of the outlet of the second expansion device 10.
- the flow rate control device 7-1 is provided between the connection point X (see FIG. 16) between the outlet of the second defrost pipe 40 and the main circuit and the indoor heat exchanger 11b functioning as an evaporator. Yes.
- the indoor unit B that performs cooling, it is required to control the “pressure for cooling (Y)” that is the refrigerant pressure of the indoor heat exchanger 11b to a target pressure corresponding to the set temperature.
- the target pressure may not be achieved because the “cooling pressure (Y)” is limited.
- this restriction is eliminated and the target pressure can be controlled.
- FIG. 18 shows the pressure of the refrigerant that is defrosted by the parallel heat exchanger 3-2 of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention, and the cooling is performed by the indoor heat exchanger 11b that functions as an evaporator.
- the positional relationship between the flow control device 7-1 and the second expansion device 10 is schematically shown.
- the vertical axis is pressure.
- 18A shows a case where the flow control device 7-1 is provided downstream of the outlet of the second throttling device 10, and FIG.
- FIG. 18B shows a case where the flow control device 7-1 shows the second throttling device 10. The case where it was provided upstream of the exit of No. is shown.
- the first embodiment corresponds to the case where the flow rate control device 7-1 in FIG. 18B is provided upstream of the outlet of the second expansion device 10.
- the defrosted refrigerant is changed from “pressure for defrosting (X)” to the second pressure.
- the pressure is reduced by the expansion device 10.
- the refrigerant decompressed by the second expansion device 10 is merged with the refrigerant that has been cooled by the indoor unit B and becomes the same as the “pressure (Y) for cooling”, and then the flow control device 7 ⁇
- the pressure is reduced at 1 to “endothermic pressure (Z)”.
- the “pressure for cooling (Y)” can be adjusted only within a range between “pressure for performing defrost (X)” and “pressure for performing endotherm (Z)”.
- the “defrosting pressure (X)” can be adjusted only within a range higher than the “cooling pressure (Y)”.
- the “pressure for cooling (Y)” can be adjusted only in a range lower than the “pressure for performing defrost (X)”.
- the “defrosting pressure (X)” is adjusted to about 0 ° C. to 10 ° C. at the saturation conversion temperature by the second expansion device 10 as described above. For this reason, the saturation conversion temperature of “pressure for cooling (Y)” that can be adjusted only at a pressure lower than “pressure for performing defrost (X)” is the saturation conversion temperature of “pressure for performing defrost (X)”. It becomes lower than 0 ° C to 10 ° C. That is, the saturation temperature of the refrigerant in the indoor heat exchanger 11b is lower than 0 ° C. to 10 ° C.
- the “pressure for cooling (Y)” corresponding to the set temperature is usually in the range of about 5 to 20 ° C. in terms of saturation temperature.
- the saturation temperature of the refrigerant in the indoor heat exchanger 11b becomes 0 ° C. or lower, frosting and freezing occur in the indoor unit B, air can not be blown into the room, and the heat exchanger may be damaged. There is sex.
- the cooling must be stopped and the room is heated by flowing a high-temperature refrigerant to the indoor heat exchanger 11b. May be reduced.
- the defrost generates a larger amount of defrost water in a shorter time than the dew condensation water during normal cooling. Therefore, the defrost water may be scattered and leaked indoors unless the drainage capacity of the drainage mechanism such as a drain pan is increased. There is.
- the defrosted refrigerant is “defrosted” as shown in FIG.
- the pressure is reduced by the second expansion device 10 from the “pressure (X) to be performed” to become “pressure to perform endotherm (Z)”.
- the cooled refrigerant is depressurized by the flow control device 7-1 from “cooling pressure (Y)” to become “endothermic pressure (Z)”. Therefore, “pressure for performing defrost (X)” and “pressure for performing cooling (Y)” can be individually adjusted. For this reason, the “pressure to perform defrosting (X)” is adjusted to about 0 ° C. to 10 ° C.
- the “pressure to perform cooling (Y)” is 0 ° C. in terms of saturation temperature. It can be adjusted within the range above and below the set temperature. Therefore, frost formation and freezing in the indoor unit B can be prevented and the room temperature can be adjusted, and the comfort in the entire room can be improved.
- the parallel heat exchangers 3-1 and 3-2 are integrated, and the outdoor air from the outdoor fan 3 f is also conveyed to the parallel heat exchanger 3-2 to be defrosted.
- the fan output may be changed according to the ratio of (cooling load) / (heating load).
- the fan output of the outdoor fan 3f is reduced and the defrost target parallel heat exchanger 3-2
- the heating capacity of the defrost is lowered by the amount of heat radiation to the air in the parallel heat exchanger 3-2, the heating capacity can be increased accordingly.
- the flow rate of the refrigerant flowing into the parallel heat exchanger 3-2 to be defrosted may be controlled according to the heating load of the indoor heat exchanger 11c functioning as a condenser. . Specifically, when the heating load is smaller than the preset set load, the opening of the first expansion device 8 is increased to increase the flow rate of the refrigerant flowing into the parallel heat exchanger 3-2. Also good. In this case, defrosting can be achieved in a short time.
- the opening degree of the flow control device 7-1 may be changed in advance according to the ratio of (cooling load) / (heating load). This will be described below.
- both the parallel heat exchangers 3-1 and 3-2 function as evaporators, and the refrigerant flowing through the main circuit flowing out from the backflow prevention device 5-4 flows through the flow control device 7-1, Branch to 7-2.
- the parallel heat exchanger 3-1 functions as an evaporator, and the refrigerant flowing through the main circuit flowing out from the backflow prevention device 5-4 passes only through the flow control device 7-1. .
- the heating main operation When the heating main operation is switched to the heating main defrost operation, the area of the outdoor heat exchanger 3 that functions as an evaporator is reduced, so that the low pressure is reduced, and the refrigerant pressure in the indoor heat exchanger 11b is reduced due to the low pressure reduction. descend. Further, when the heating main normal operation is switched to the heating main defrost operation, the refrigerant on the refrigerant inflow side of the flow control device 7-1 is changed by switching so that all of the refrigerant passing through the main circuit passes only through the flow control device 7-1. It increases and the pressure of the refrigerant
- the refrigerant pressure decrease factor of the indoor heat exchanger 11b due to the reduction in the area functioning as an evaporator and the presence / absence of branching in the flow rate control devices 7-1 and 7-2.
- the refrigerant pressure in the indoor heat exchanger 11b changes abruptly due to two factors, the cause of the increase in the refrigerant pressure in the indoor heat exchanger 11b.
- the influence of the decrease factor or the increase factor is related to the ratio of (cooling load) / (heating load).
- the heating-main normal operation when the ratio of (cooling load) / (heating load) is small, the amount of heat absorbed from the outside air in the outdoor heat exchanger 3 is the room in the indoor heat exchanger 11b of the indoor unit B that performs cooling. More than the amount of heat absorbed from the air. For this reason, the influence by the area which functions as an evaporator among the outdoor heat exchangers 3 changes is large.
- the heating main operation is switched to the heating main defrost operation, the area of the outdoor heat exchanger 3 that functions as an evaporator is reduced, so that the refrigerant pressure in the indoor heat exchanger 11b is reduced.
- the opening degree of the flow control device 7-1 is reduced in advance before the heating main By switching to the defrost operation, a decrease in the pressure of the refrigerant in the indoor heat exchanger 11b is suppressed.
- the amount of heat absorbed from the outdoor air in the outdoor heat exchanger 3 is the amount of heat absorbed by the indoor heat exchanger 11b of the indoor unit B that performs cooling. Less than the amount of heat absorbed from the room air. For this reason, the influence by the change of the area which functions as an evaporator among the outdoor heat exchangers 3 becomes small.
- the increase in the amount of heat absorbed from the indoor air in the indoor unit B that performs cooling increases the dryness of the refrigerant that passes through the main circuit, thereby affecting the presence or absence of branching in the flow control devices 7-1 and 7-2. growing.
- the following control is performed according to the ratio of (cooling load) / (heating load).
- the ratio of (cooling load) / (heating load) is smaller than a preset second set ratio: the opening degree of the flow control device 7-1 is reduced before switching.
- the ratio of (cooling load) / (heating load) is larger than a preset second set ratio: the opening degree of the flow control device 7-1 is increased before switching.
- the following control is performed according to the ratio of (cooling load) / (heating load).
- the ratio of (cooling load) / (heating load) is smaller than a preset second setting ratio: the opening degree of the flow control device 7-1 is increased in advance before switching.
- the ratio of (cooling load) / (heating load) is larger than the preset second set ratio: the opening degree of the flow control device 7-1 is reduced before switching.
- the opening degree of the flow rate control device 7-1 By controlling the opening degree of the flow rate control device 7-1 as described above, it is possible to suppress a sudden pressure fluctuation of the refrigerant in the indoor heat exchanger 11b due to switching of the operation mode, and to improve indoor comfort.
- the control for increasing or decreasing the opening degree of the flow control device 7-1 in advance before switching is made larger or smaller than the opening degree before switching. Meaning.
- the opening degree of the flow control device 7-1 before switching is controlled according to the set temperature of the indoor unit B during cooling as described above.
- defrosting can be performed without stopping heating in the simultaneous cooling and heating operation in which cooling and heating are performed simultaneously. Further, since the second expansion device 10 and the third expansion device 19 are individually controlled, the comfort in both the cooling and heating rooms can be improved.
- FIG. FIG. 19 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of the air-conditioning apparatus 101 according to Embodiment 2 of the present invention.
- the air conditioner 101 according to the second embodiment has a configuration in which the refrigerant pressure sensor 91 is deleted from the configuration of the air conditioner 100 according to the first embodiment, and temperature sensors 92b and 92c that measure the temperature in each room are added.
- Temperature sensors 92b and 92c detect the temperature of the air flowing into the indoor heat exchangers 11b and 11c.
- the temperature sensors 92b and 92c only need to detect the temperature to be cooled.
- the cooling target temperature in addition to the temperature of the indoor air, for example, the ambient temperature of the controller such as a remote controller for starting and stopping the indoor units B and C, changing the set temperature, etc., the surface of the indoor floor, wall, etc. You may make it detect temperature etc.
- thermosensor 92b and 92c in the second embodiment correspond to the “temperature detection device” of the present invention.
- the opening degree of the flow rate control devices 7-1 and 7-2 is controlled by the control device 90 so as to adjust the room temperature detected by the temperature sensor 92b of the indoor unit B that performs cooling to the set temperature.
- the control device 90 increases the opening degree of the flow control devices 7-1 and 7-2 when the room temperature detected by the temperature sensor 92b is higher than the set temperature.
- the saturation pressure of the refrigerant in the indoor heat exchanger 11b is lowered by reducing the pressure of the refrigerant in the indoor heat exchanger 11b so as to approach the pressure of the refrigerant in the parallel heat exchangers 3-1, 3-2.
- the temperature of the air cooled by the indoor heat exchanger 11b and sent to the room is lowered, and the room temperature can be brought close to the set temperature.
- the opening degree of the flow rate control devices 7-1 and 7-2 is decreased, and the pressure of the refrigerant in the indoor heat exchanger 11b is increased to increase the indoor heat exchanger. Increase the saturation temperature of the refrigerant of 11b. As a result, the temperature of the air sent into the room is raised to bring the room temperature closer to the set temperature.
- the control device 90 increases the change width of the opening degree of the flow rate control devices 7-1 and 7-2.
- coolant of the indoor heat exchanger 11b can be changed a lot, and indoor temperature can be brought close to preset temperature quickly.
- the range of change in the opening of the flow rate control devices 7-1 and 7-2 is reduced.
- coolant of the indoor heat exchanger 11b can be made small, and it can prevent that indoor temperature changes more than a temperature difference with setting temperature.
- the indoor temperature detected by the temperature sensor 92c is used instead of the temperature sensor 92b.
- the opening degree of the flow control device 7-1 is controlled by the control device 90 so as to adjust the indoor temperature detected by the temperature sensor 92b of the indoor unit B that performs cooling to the set temperature.
- the control device 90 increases the opening degree of the flow control device 7-1 when the indoor temperature detected by the temperature sensor 92b is higher than the set temperature. Thereby, the saturation pressure of the refrigerant in the indoor heat exchanger 11b is lowered by lowering the pressure of the refrigerant in the indoor heat exchanger 11b and bringing it closer to the pressure of the refrigerant in the parallel heat exchanger 3-1. As a result, the temperature of the air cooled and sent indoors by the indoor heat exchanger 11b is lowered, and the indoor temperature can be brought close to the set temperature.
- the opening degree of the flow control device 7-1 is decreased, the refrigerant pressure in the indoor heat exchanger 11b is increased, and the refrigerant in the indoor heat exchanger 11b is increased. Increase the saturation temperature. As a result, the temperature of the air sent into the room is raised to prevent the room temperature from becoming lower than the set temperature.
- the control device 90 increases the range of change in the opening degree of the flow rate control device 7-1.
- coolant of the indoor heat exchanger 11b can be changed a lot, and indoor temperature can be brought close to preset temperature quickly.
- the range of change in the opening degree of the flow control device 7-1 is reduced. Thereby, the change of the saturation temperature of the refrigerant
- the indoor temperature detected by the temperature sensor 92c is used instead of the temperature sensor 92b.
- the opening degree of one or both of the flow rate control devices 7-1 and 7-2 is as follows. Be controlled. That is, the flow rate control devices 7-1 and 7-2 control the room temperature detected by the temperature sensor provided in the room for cooling among the temperature sensors 92b and 92c so as to adjust the set temperature in the room. Controlled by device 90. Thereby, the indoor temperature of cooling can be adjusted to preset temperature, and indoor comfort can be improved.
- FIG. 20 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of the air-conditioning apparatus 102 according to Embodiment 3 of the present invention.
- the air conditioning apparatus 102 will be described with a focus on differences from the first embodiment.
- the air conditioner 102 according to the third embodiment includes the third switching devices 18-1 and 18-2 instead of the flow rate control devices 7-1 and 7-2 in the configuration of the air conditioner 100 according to the first embodiment. Is provided. Further, a third throttling device 19 is provided between the third switching devices 18-1 and 18-2 and the backflow prevention device 5-4 and between the third switching devices 18-1 and 18-2 and the refrigerant pressure sensor 91. Has been added.
- the third opening / closing devices 18-1 and 18-2 in the third embodiment correspond to the “second flow path switching device” of the present invention, and the third expansion device 19 is the “second flow switching device” of the present invention. This corresponds to a “third aperture device”.
- the third opening / closing devices 18-1 and 18-2 are opened, and the third expansion device 19 is fully opened.
- the refrigerant flowing out from the parallel heat exchangers 3-1 and 3-2 passes through the third switching devices 18-1 and 18-2 and then passes through the third expansion device 19. It flows into the backflow prevention device 5-1. Since the third expansion device 19 is in a fully opened state, there is almost no decompression or expansion of the refrigerant.
- the third opening / closing devices 18-1 and 18-2 are opened, and the third expansion device 19 has a constant opening.
- the refrigerant flowing out of the backflow prevention device 5-4 is squeezed by the third throttling device 19 to expand and depressurize, and after reaching a low pressure, it is branched into two, and the third switching device 18- 1, 18-2.
- the third throttling device 19 is fixed at a constant opening, for example, fully opened, or the saturation temperature of the intermediate pressure of the second extension pipe 32 detected by the refrigerant pressure sensor 91 is 0 ° C. to 20 ° C. You may control so that it may become a grade. By controlling the saturation temperature of the intermediate pressure of the second extension pipe 32 or the like, condensation or icing on the pipe surface can be prevented.
- the third opening / closing devices 18-1 and 18-2 are opened, the third throttling device 19 is opened, and the refrigerant flowing out from the backflow prevention device 5-4 is squeezed and expanded by the third throttling device 19.
- the pressure is reduced, and after the pressure is reduced, it is branched into two and flows into the third switching devices 18-1 and 18-2.
- the opening of the third expansion device 19 is set so that the refrigerant pressure in the indoor heat exchanger 11b functioning as an evaporator detected by the refrigerant pressure sensor 91 is a target pressure corresponding to the set temperature or the like. It is controlled by the control device 90. Thereby, the saturation temperature of the refrigerant of the indoor heat exchanger 11b that performs cooling can be adjusted, and the temperature of the air that is cooled by the indoor heat exchanger 11b and sent indoors can be adjusted. For this reason, the driving
- the parallel heat exchanger 3-2 performs defrosting
- the parallel heat exchanger 3-1 functions as an evaporator
- the indoor unit B performs cooling
- the indoor unit C performs heating
- the third opening / closing device 18-1 is opened, the third throttling device 19 is opened, and the refrigerant flowing out from the backflow prevention device 5-4 is throttled by the third throttling device 19 so as to expand and depressurize. Then, it flows only into the third switching device 18-1.
- the third opening / closing device 18-2 is closed to stop the flow of refrigerant from the backflow prevention device 5-4 to the parallel heat exchanger 3-2 to be defrosted.
- the opening of the third expansion device 19 is set so that the refrigerant pressure in the indoor heat exchanger 11b functioning as an evaporator detected by the refrigerant pressure sensor 91 is a target pressure corresponding to the set temperature or the like. It is controlled by the control device 90.
- the saturation temperature of the refrigerant of the indoor heat exchanger 11b that performs cooling can be adjusted, and the temperature of the air that is cooled by the indoor heat exchanger 11b and sent to the room can be adjusted. It is possible to drive in conformity with the driving comfort and improve indoor comfort.
- the evaporator is controlled by controlling the opening degree of the third expansion device 19 regardless of which of the parallel heat exchangers 3-1 and 3-2 is defrosted.
- the pressure of the refrigerant in the functioning indoor heat exchanger 11b is adjusted.
- the pressure of the refrigerant functioning as the evaporator among the indoor heat exchangers 11b and 11c is changed to the third pressure.
- This is controlled only by the diaphragm device 19.
- it is possible to reduce the number of valves whose opening degree can be controlled, which are used for adjusting the refrigerant flow rate and pressure.
- the second embodiment shown in FIG. 19 requires three flow rate control devices 7-1 and 7-2 and the second throttling device 10, whereas the present embodiment shown in FIG. In the third embodiment, the number can be reduced to two, that is, the second diaphragm device 10 and the third diaphragm device 19.
- valves whose opening degree can be controlled are reduced, the number of opening and closing devices has been increased to two, the opening and closing apparatuses are often cheaper than valves whose opening degree can be controlled. For this reason, even if the number of opening / closing devices increases, the number of valves whose opening degree can be controlled can be reduced, so that an effect of reducing the cost can be expected, and the control can be simplified.
- the third expansion device 19 is provided upstream of the second expansion device 10, as described with reference to FIG. 18, the pressure of the parallel heat exchanger 3-1 or 3-2 that performs defrosting and cooling are performed.
- the pressure of the indoor heat exchanger 11b or 11c can be adjusted individually.
- the outdoor heat exchanger 3 is divided into two parallel heat exchangers 3-1 and 3-2 has been described.
- the present invention is not limited to this. .
- Even in a configuration including three or more parallel heat exchangers by applying the above-described inventive concept, some parallel heat exchangers are targeted for defrosting, and heating operation is continued with some other parallel heat exchangers. Can be operated to.
- Embodiments 1, 2, and 3 the case where there are two indoor heat exchangers has been described, but the present invention is not limited to this. Even in a configuration including three or more indoor units, by applying the inventive idea described above, the pressure of the refrigerant of the parallel heat exchanger to be defrosted and the pressure of the refrigerant of the indoor heat exchanger functioning as an evaporator can be individually set. Can be operated to adjust.
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Abstract
Description
なお、各図において、同一の符号を付したものは、同一の又はこれに相当するものであり、これは明細書の全文において共通している。
更に、明細書全文に表れている構成要素の形態は、あくまで例示であってこれらの記載に限定されるものではない。
図1は、本発明の実施の形態1に係る空気調和装置100の冷媒回路構成を示す冷媒回路図である。
空気調和装置100は、室外機(熱源機、熱源側ユニット)Aと、互いに並列に接続された複数の室内機(負荷側ユニット)B、Cと、中継機Dを備えている。室外機Aと中継機Dとは、高圧配管である第1の延長配管31、低圧配管である第2の延長配管32で接続されている。中継機Dと室内機B、Cとは第3の延長配管33b、33c、第4の延長配管34b、34cで接続されている。
空気調和装置100は、圧縮機1と、室内熱交換器11b、11cと、減圧装置である室内流量制御装置12b、12cと、並列熱交換器3-1、3-2で構成された室外熱交換器3と、が順次、配管で接続された主回路を有している。
室外機Aは圧縮機1と、流路切替装置2と、室外熱交換器3と、アキュムレータ4と、逆流防止装置5-1、5-2、5-3、5-4を有しており、これらが配管で接続された回路が主回路の一部である。アキュムレータ4は必ずしも必須ではなく、省略しても良い。
室内機B及び室内機Cは例えば同一の構成を有するものである。室内機Bは、室内熱交換器11bと、室内流量制御装置12bとを備えている。また、室内機Cは、室内熱交換器11cと、室内流量制御装置12cとを備えている。室内機Bに備えられた各機器と室内機Cに備えられた各機器とが配管で接続された回路が主回路の一部である。また、室内流量制御装置12b及び室内流量制御装置12cは、本発明の「減圧装置」に相当する。
中継機Dは気液分離装置13と、第1の中継開閉装置14b、14cと、第2の中継開閉装置15b、15cと、第1の中継流量制御装置16と、第2の中継流量制御装置17とを有しており、これらが配管で接続された回路が主回路の一部である。
図6は、本発明の実施の形態1に係る空気調和装置100の全冷房運転時の冷媒の流れを示す図である。図6において全冷房運転時に冷媒が流れる部分を実線とし、冷媒が流れない部分を破線としている。なお、図6では室内機B、Cが冷房を行っている場合を示している。
図8は、本発明の実施の形態1に係る空気調和装置100の冷房主体運転時の冷媒の流れを示す図である。図8において冷房主体運転時に冷媒が流れる部分を実線とし、冷媒が流れない部分を破線としている。なお、図8では室内機Bが冷房、室内機Cが暖房を行っている場合を示している。以降の実施の形態の説明においても同様に、室内機Bが冷房、室内機Cが暖房を行っている場合について説明する。室内機Bが暖房、室内機Cが冷房を行う場合は、室内流量制御装置12b、12c、第1の中継開閉装置14b、14c、第2の中継開閉装置15b、15cの開閉状態が逆転し、室内機Bと室内機Cの冷媒の流れが入れ替わるだけで、その他の動作は同じとなる。
図10は、本発明の実施の形態1に係る空気調和装置100の全暖房通常運転時の冷媒の流れを示す図である。なお、図10において全暖房通常運転時に冷媒が流れる部分を実線とし、冷媒が流れない部分を破線としている。なお、図10では室内機B、Cが暖房を行っている場合を示している。
図12は、本発明の実施の形態1に係る空気調和装置100の暖房主体通常運転時の冷媒の流れを示す図である。なお、図12において暖房主体通常運転時に冷媒が流れる部分を実線とし、冷媒が流れない部分を破線としている。なお、図12では室内機Bが冷房、室内機Cが暖房となっている場合を示している。室内機Bが暖房、室内機Cが冷房を行う場合は、室内流量制御装置12b、12c、第1の中継開閉装置14b、14c、第2の中継開閉装置15b、15cの開閉状態が逆転し、室内機Bと室内機Cの冷媒の流れが入れ替わるだけで、その他の動作は同じとなる。
全暖房デフロスト運転は、全暖房通常運転中に、室外熱交換器3に着霜した場合に行われる。もしくは、暖房主体デフロスト運転中に冷房を行う室内機が停止し、運転中の室内機が全て暖房になった場合も全暖房デフロスト運転となる。
暖房主体デフロスト運転は、暖房主体通常運転中に、室外熱交換器3に着霜した場合に行われる。もしくは、全暖房デフロスト運転中に室内機の一部で冷房が開始された場合も暖房主体デフロスト運転となる。
(1)(冷房負荷)/(暖房負荷)の比が予め設定した第2設定比より小さい場合:流量制御装置7-1の開度を切替前に予め小さくする。
(2)(冷房負荷)/(暖房負荷)の比が予め設定した第2設定比より大きい場合:流量制御装置7-1の開度を切替前に予め大きくする。
(3)(冷房負荷)/(暖房負荷)の比が予め設定した第2設定比より小さい場合:流量制御装置7-1の開度を切替前に予め大きくする。
(4)(冷房負荷)/(暖房負荷)の比が予め設定した第2設定比より大きい場合:流量制御装置7-1の開度を切替前に予め小さくする。
図19は、本発明の実施の形態2に係る空気調和装置101の冷媒回路構成を示す冷媒回路図である。
本実施の形態2における暖房主体通常運転時について、実施の形態1と異なる部分について説明する。ここでは、室内機Bが冷房、室内機Cが暖房を行う場合について説明する。
次に、本実施の形態2における暖房主体デフロスト運転について、実施の形態1と異なる部分を説明する。ここでは、並列熱交換器3-2がデフロストを行い、並列熱交換器3-1が蒸発器として機能し、室内機Bが冷房、室内機Cが暖房を行う場合について説明する。
図20は、本発明の実施の形態3に係る空気調和装置102の冷媒回路構成を示す冷媒回路図である。
Claims (12)
- 圧縮機と、複数の室内熱交換器と、複数の減圧装置と、複数の並列熱交換器で構成された室外熱交換器と、が順に配管で接続された主回路と、
前記圧縮機から吐出された冷媒の一部を、前記主回路から分岐して前記複数の並列熱交換器のうちデフロスト対象の前記並列熱交換器に供給する第1のデフロスト配管と、
前記第1のデフロスト配管に設けられた第1の絞り装置と、
前記第1のデフロスト配管を介してデフロスト対象の前記並列熱交換器に供給された冷媒を、前記主回路に戻す第2のデフロスト配管と、
前記複数の並列熱交換器の各々における前記圧縮機側の接続を、前記第1のデフロスト配管又は前記主回路に切り替える第1の流路切替装置と、
前記複数の並列熱交換器の各々における前記圧縮機と反対側の接続を、前記第2のデフロスト配管又は前記主回路に切り替える第2の流路切替装置と、
前記第2のデフロスト配管に設けられ、デフロスト対象の前記並列熱交換器の冷媒圧力を調整する第2の絞り装置と、
前記第2のデフロスト配管の出口と前記主回路との接続点と前記複数の室内熱交換器のうち蒸発器として機能する前記室内熱交換器との間に設けられ、蒸発器として機能する前記室内熱交換器の冷媒圧力を調整する第3の絞り装置と、
前記第1の絞り装置、前記第2の絞り装置、前記第3の絞り装置を制御する制御装置とを備え、
前記制御装置は、前記圧縮機から吐出された冷媒の一部を前記第1のデフロスト配管及び前記第2のデフロスト配管を介してデフロスト対象の前記並列熱交換器に通過させると共に、前記複数の並列熱交換器において前記デフロスト対象の並列熱交換器以外を蒸発器として機能させ、また、前記複数の室内熱交換器のうち一部を蒸発器、その他を凝縮器として機能させる第1運転時に、前記第2の絞り装置と前記第3の絞り装置とをそれぞれ個別に制御する空気調和装置。 - 前記制御装置は、前記第1運転時に、蒸発器として機能する前記室内熱交換器を有する室内の設定温度に基づいて前記第3の絞り装置を制御する請求項1記載の空気調和装置。
- 前記第1運転時に、蒸発器として機能する前記室内熱交換器の冷媒の圧力を検知する圧力検知装置を備え、
前記制御装置は、前記圧力検知装置で検知した冷媒圧力が、前記設定温度に応じた目標圧力となるように前記第3の絞り装置を制御する請求項2記載の空気調和装置。 - 前記目標圧力は、飽和温度換算で0℃以上かつ前記設定温度以下である請求項3記載の空気調和装置。
- 蒸発器として機能する前記室内熱交換器の冷却対象の温度を検知する温度検知装置を備え、
前記制御装置は、前記温度検知装置で検知された温度と前記設定温度との高低関係に基づいて前記第3の絞り装置を制御する請求項2記載の空気調和装置。 - 前記制御装置は、前記温度検知装置で検知された温度が前記設定温度よりも高い場合、前記第3の絞り装置の開度を大きくし、前記温度検知装置で検知された温度が前記設定温度よりも低い場合、前記第3の絞り装置の開度を小さくする請求項5記載の空気調和装置。
- 前記複数の並列熱交換器に外気を搬送するファンを備え、
前記制御装置は、前記第1運転中、前記複数の室内熱交換器のうち、蒸発器として機能する前記室内熱交換器の冷房負荷を、前記複数の室内熱交換器のうち、凝縮器として機能する前記室内熱交換器の暖房負荷で除算した比に応じて、前記ファンの出力を制御する請求項1~請求項6の何れか一項に記載の空気調和装置。 - 前記制御装置は、前記比が予め設定した第1設定比よりも大きい場合、前記ファンの出力を低減する請求項7記載の空気調和装置。
- 前記制御装置は、前記第1運転中、前記複数の室内熱交換器のうち、凝縮器として機能する前記室内熱交換器の暖房負荷に応じて前記第1の絞り装置を制御する請求項1~請求項8の何れか一項に記載の空気調和装置。
- 前記制御装置は、前記第1運転中、前記暖房負荷が予め設定した設定負荷よりも小さい場合には、前記第1の絞り装置の開度を大きくする請求項9記載の空気調和装置。
- 前記第1運転と、前記複数の並列熱交換器の全てが蒸発器として機能し、且つ前記複数の室内熱交換器のうち一部が蒸発器、その他が凝縮器として機能する第2運転とを切り替える際、前記制御装置は、前記複数の室内熱交換器のうち、蒸発器として機能する前記室内熱交換器の冷房負荷を、前記複数の室内熱交換器のうち、凝縮器として機能する前記室内熱交換器の暖房負荷で除算した比に応じて前記第3の絞り装置を制御する請求項1~請求項10の何れか一項に記載の空気調和装置。
- 前記制御装置は、
前記第1運転から前記第2運転へ切り替える際には、
前記比が予め設定した第2設定比よりも小さい場合、前記第3の絞り装置の開度を切替前に予め小さくし、
前記比が前記第2設定比よりも大きい場合、前記第3の絞り装置の開度を切替前に予め大きくし、
前記第2運転から前記第1運転へ切り替える際には、
前記比が前記第2設定比よりも小さい場合、前記第3の絞り装置の開度を切替前に予め大きくし、
前記比が前記第2設定比よりも大きい場合、前記第3の絞り装置の開度を切替前に予め小さくする請求項11記載の空気調和装置。
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Also Published As
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CN109154463B (zh) | 2020-11-10 |
GB2563776A (en) | 2018-12-26 |
JPWO2017199289A1 (ja) | 2018-11-22 |
DE112016006864T5 (de) | 2019-02-14 |
CN109154463A (zh) | 2019-01-04 |
US20190107314A1 (en) | 2019-04-11 |
US10808976B2 (en) | 2020-10-20 |
GB2563776C (en) | 2020-12-02 |
JP6576552B2 (ja) | 2019-09-18 |
GB2563776B (en) | 2020-11-04 |
DE112016006864B4 (de) | 2023-02-16 |
GB201814961D0 (en) | 2018-10-31 |
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